Inertia type brake control means



Jan. 21, 1941. 1 Q MccuNE INERTIA TYPE BRAKE CONTROL MEANS Filed Dec.

2 Sheets-Sheet l NvENToR JOSEPH C. MCCUNE BY I l w ATTORNEY Jan. 21, 1941. J. c. MccuNE 2,229,514

INERTIA TYPE BRAKE QONTROL SANS Filed Dec. 31, 193B 2 Sheets-Sheet 2 47 .F @IZ :67

45 INVENTOR 46 JOEEFH C MCCUNE 33 ATTORNEY Patented Jan. 21, 1941 PATENT OFFICE INERTIA TYPE BRAKE CONTROL li/IEANS Joseph C. McCune, Edgewood, Pa., assignor to The Westinghouse Air Brake Company, Wilmerding, Pa., a corporation of Pennsylvania Application December 31, 1938, Serial No. 248,653

10 Claims.

This invention relates to inertia type brake control means for vehicles such as railway cars and trains, and has particular relation to rotary inertia means associated individually with each Wheel or plurality of Wheels of a car or train for regulating the rate of retardation of the train to a substantially uniform rate and also effective to prevent sliding of the individual Wheels in the event that they begin to slip.

In my prior Patent 2,132,959 and my prior copending application Serial No. 248,654 led December 3l, 1938, brake control equipments are disclosed including rotary inertia devices associated with the individual Wheels or wheel axles of a car or train and effective to regulate and control the brakes on the train so as to cause a substantially uniform rate of retardation and also operative in the event that an individual Wheel slips for preventing the sliding of the Wheel. These equipments are adapted primarily to the control of brakes employing the usual metallic or cast iron brake shoes adapted to frictionally engage the rim or tread of the car Wheels. As is well known, the coeiicient of friction of metallic brake shoes increases as the speed of the rotation of the car Wheel decreases, it thus being essential that the brake cylinder pressure be reduced as the speed of the car or train reduces in order to maintain a substantially uniform rate of retardation of the car or train.

The brake control equipment constituting my present invention is adapted to be employed in connection With brake equipments including brake shoes or the equivalent thereof of a material such that the coeiiicient of friction between the shoes and the rim or other braking surface of the car wheel diminishes or fades with the continued application of the brakes. Brake shoes having a friction surface of composition material, such as liber or molded material, possess this socalled friction-fading characteristic. The brake control equipment constituting my present invention is accordingly adapted to the peculiar requirements of brake devices having a friction-fading characteristic and functions automatically to compensate for the reduction in the coenicient of friction of brake shoes or other rubbing parts of the brake devices, in such manner as to cause the car or train to be retarded at a substantially constant or uniform rate of retardation.

My proposed brake control equipment is furthermore adapted to be applied to cars having individually rotatable fheels. It will be appreciated that since the Weight of an individual car Wheel is a fraction of the weight of a pair of car wheels fixed to an axle, that the individually rotatable car Wheel will decelerate rotatively toward a lock-ed-wheel or sliding condition, once it begins to slip, at a much faster rate than in 5 the case of a pair of car wheels connected by an axle. In order to prevent a car Wheel of the individually rotatable type from attaining a locked-Wheel or sliding condition once it begins to slip, it is essential that exceedingly sensitive 10 means be provided for rapidly releasing the brakes on the slipping wheel substantially at the instant that they begin to slip. This is particularly true when the car wheel is rotating at low speed. The brake control equipment constitut- 15 ing my present invention accordingly includes an arrangement for differentiating between the rotative deceleration of the car Wheels at a high rate Without slipping and the rotative deceleration of the car Wheels at a low rate While slipping. More specifically, my proposed brake control equipment includes a device responsive to the retardation of the car or train for causing the rotary inertia devices associated With the individual car Wheels to operate at a relatively 10W rate of rotative deceleration to prevent sliding of the car wheels when the rate of retardation of the car or train is less than a certain rate and to cause the rotary inertia devices associated with the individual car wheels to operate only at a much higher rate of deceleration to prevent sliding of the car Wheels when the rate of retardation of the train exceeds the certain rate.

It is accordingly an object of my invention to provide a brake control equipment adapted to be employed in connection with brake devices having cooperating friction elements possessing friction-fading characteristics and adapted to function automatically to compensate for the fading coefficient of friction of the rubbing parts of the brake devices and thereby so regulate the application of the brakes as to cause a substantially uniform rate of retardation of the car or train to be maintained.

Another object of my invention is to provide a brake control arrangement including rotary inertia devices associated individually with each car Wheel and a device responsive to the rate of retardation of the car or train, adapted so that when the retardation of the car or train is less than a certain rate, the rotary inertia devices are responsive to a certain low rate of rotative' deceleration of the car wheels to guard against sliding of the car Wheels and so that When the rate of retardation of the car or train exceeds the certain rate, the rotary inertia devices are operatively sensitive to a higher rate of rotative deceleration to guard against sliding of the car Wheels.

the retardation switch; and a relay 2l', hereinafter called the retardation relay, is operatively controlled by energization and deenergization of the retardation wire to modify operation of ffl 5 The above objects and other objects of my nthe rotary inertia device I6 according to the vention which will be made apparent hereinafter operation of the retardation switch 2t in the are obtained by means of an illustrative brake control exercised by the rotary inertia devices control equipment subsequently to be described over the slip magnet valve I'I. and Shown in the accompanying drawings A pressure switch 28, controlled by the pres-- l wherein sure in the brake pipe and hereinafter called lil Fig. 1 is a diagrammatic simplified arrangethe emergency protection switch is provided for ment embodying my invention, a purpose to be hereinafter made apparent.

Fig. 2 is a fragmental vertical sectional view ASSOCieteCl With the reapplieatiu magnet showing an individually rotatable car Wheel and ValVe I3 iS al Supply reSelVOir 3l rOm Which l5 the details of a rotary inertia device associated fluid under pressure is supplied ISO the brake l5 therewith, cylinder I4 under the control of the reapplica- Fig. 3 is a fragmental sectional View taken on tion magnet valve I8 in the manner to be herethe line 3 3 of Fig. 2, showing further details of inafter ciescribecilr additional eqviplrlent inthe rotary inertia devices, and cludes a source of electrical energy, such as the Fig. 4 is a fragmental sectional View showing a Sterage battery 32, and 2L pressure switch 33 asmodincation or the cut-orf magnet valve illussoeated therewith for preventing the supply of trated in Fig. 1. current from the battery 32 except during an application of the brakes. BRIEF DESCRIPTION or EQUIPMENT l DETAILED DESCRIPTION or EQUIPMENT Q5 Referring to Fig. l, the brake control equipment shown includes that for a single car, it The Various Darts Of l'Ille equipment ulOOVe being understood that that for other cars of the bleily mentioned Will 110W he Considered and detrain substantially duplicates that illustrated. SCIllOeCl in detall- Brake pipe II iS normally The brake control equipment shown in Fig. l Charged ISO 2 given pressure, Such as ninety .,O

comprises a conventional automatic air brake pounds per Square inch, in the conventional equipment including a brake pipe II extending 1119111191' from a Suitable SOuCe O Supply eS from car to car throughout the train, a brake under the Cerr'rl of standard brake Valve of controlling valve device I2, illustrated as the lille automatic type, not Sho-Wn. As is Well underfamiliar triple valve, an auxiliary reservoir I3 stood by those skilled in the art, the automatic and a brake cylinder is brake valve is manually operated and includes "fd For simplicity, only one car wheel I5 is shown au Operating handle Which is adapted to be but it Shomd be understood that a plurality of moved out of a normal release position to a servwheels are provided for the car mounted in a iCe uppliCatiOh pOSiliOll, e lap pOSliOn, 0r au plurality of wheel trucks. For simplicity, only emergency pOSlIOll. When the brake valve han- -40 one broke oyundor M is Shown in associated dle is shifted to a service application position, Ai0

relation with the car wheel I5 for operating the the pressure i11 the brake pipe I I is reduced at a wheel brakes. It should be understood however Service rute and When the handle is shifted to that a plurality of brake cylinders connected in fr lap p0Si0i01 ullller reduCiOll O Jhe pressure parallel relation may be provided for each wheel m the b1 alie pipe CeaSeS- When the brake Valve trucky @ouch brake cylinder being effective to handle is shifted to an emergency position, the 45 operate the brakes of an associated wheel or DFeSSU-le in lShe brake pipe II is reduced at an plurality of wheels. emergency rate.

A rotary inertia, dovoo i6, djogmmmatoouy The brake controlling valve device I2 is illusindicated in Fig. 1 ood Shown in detail in Figo trated as the standard triple valve and should,

2 and 3, is provided in associated relation with tlle'eOTe, refiuile nO CleSCrptiGn Since the Con- 5o each car wheel I5, which rotary inertia device 'struction and Operation 0f the triple Valve is is operatively responsive to the rate of rotative Well lIlOWu- Breily however, the Jtriple Valve deceleration or acceleration of the individual i2 has e piSOrl Chamber Which is Constantly car wheel with which itis associated. The rotary @Omleted 't0 the brake pipe I I through a branch D5 inertia devices I6 are effective to control the pipe Ila and the piston of the triple valve is 55 operation of a slip magnet valve device I'I, a reeffective in response to the normal pressure in application magnet valve device g3 and a @M the brake pipe to condition the slide valves of off magnet volvo device ig the triple valve so as to effect release of iiuid Extending from oar to oar throughout the under pressure from the brake cylinder supply train are o, pair of train Wires 2g and 22, the pipe 35 and the charging of the auxiliary reser- 60 Vire hereafter Called the synchronizing VOlI t0 the pressure established. the brake wire and the wire Z22 being called the retarda- P1199- Upon a Service reduCiiOrl 0f the pressure tion Wiyo in the brake pipe, the operating piston of the The synchronizing Wire gl is energized onder triple valve responds to the reduction of pres- 55 the control of the rotary inertia devices I6; and Sure acl/ing thereOrl t0 Shift the Slide valves of 65 a relay 23, hereinafter called the synchronizing the triple Valve S0 as .to'establish communicarelay, is operatively controlled by energization lilOI-l through WlliCh fluld undef pressure iS Supand deenergization of the synchronizing wire plied frOm the auxiliary reservoir I3 to the to in turn control a relay 213, hereinafter called brake Cylinder Supply pipe 35.

the stick relay, which in turn controls the As is Well understood, the triple Valve I2 is 70 operation oi the cut-oir magnet valve I9. Operative to establish a pressure in the brake The retardation wire 22 is energized and cie- Cylinder Supply pipe 35. which corresponds to the energized under the control of a switch device amount of reduction of the pressure in the brake 2l] operatively responsive to the rate of retardapipe, the triple valve automatically lapping ol tien of the car or train and hereinafter called the supply pressure from the auxiliary reservoir. 75

When the pressure in the brake pipe II is reduced at an emergency rate, the triple valve operates to supply iiuid under pressure from the auxiliary reservoir to the brake cylinder pipe 35 at an emergency rate. Furthermore, the triple valve does not lap the supply communication from the auxiliary reservoir and a maximum pressure is established in the brake cylinder pipe 35 corresponding to the pressure of equalization between the auxiliary reservoir and the connected brake cylinder pipe 35. For simplicity, the brake cylinder supply pipe 35 will be conisdered hereinafter as extending to the brake cylinder I4, the cut-off magnet valve I9 and the slip magnet Valve I1 being interposed in the brake cylinder pipe 35 and operative to control the brake cylinder pressure in the manner to be hereinafter described.

The rotary inertia devices I6 associated with each individual car wheel I may be .of any suitable construction but are illustrated in Figs. 2 and 3 as one of the types described and claimed in my pending application Serial No. 255,649, filed February 10, 1939. Referring to Figs. 2 and 3, the rotary inertia device I6 may comprise a rotary inertia element or ring 31, hereinafter referred to as the inertia ring, rotatably mounted on the inner end of the hub portion 3B of the car wheel I5. The car wheels I5 are suitably mounted for individual and separate rotation, as for example Ain the manner shown, on a nonrotatable axle 39 fixed in the frame of the wheel truck, ball-bearing members 4I being interposed in the central opening in the hub portion 38 of the wheels.

The inertia ring 31 is adapted to be driven by rotation of a car wheel through a flexible yielding connection in the form of a leaf spring 42 which is fixed by an insulating connection at the outer end to the inertia ring and at the inner end to a tubular member 43 which is secured as by screws 44 to the inner end of the hub portion 33 of car wheel I5.

The tubular member 43 has a portion at one end which surrounds the inner end of the hub portion 38 of the car wheels and secured to this portion of the tubular member 43 is a bearing ring 45. Interposed between the tubular member 43 and the bearing ring 45 is an annular cushioning ring 46 of suitable material Vsuch as rubber, the cushioning ring 46 being bonded on the outer surface thereof to the bearing ring 45 and on the inner surface thereof to the tubular member 43 so that the bearing ring 45 is securely fastened to the tubular member 43.

The bearing ring 45 and the inertia ring 31 are provided with complementary peripheral grooves 48 and 41, respectively, the grooves being preferably of semi-hexagonal contour in crosssection and containing a plurality of ball bearings 49 whereby the inertia ring 31 is rotatably supported on and interlocked with the inner end of the hub portion 38 of the car wheel. The ballbearings 49 are introduced into the complementary grooves 41 and 48 through a transverse slot 5I in the inertia ring 31 and held individually in fixed peripheral positions in spaced relation to each other by forked members 52 secured as by screws 53 to one edge of the inertia ring and extending into the space between the inertia ring and the bearing ring in a manner to straddle the corresponding ball-bearing 49.

The inertia ring 31 is provided with a lug 55 that extends radially inward between a pair of spaced lugs 56, only one of which is indicated in Fig. 2, formed on or fixed to the bearing ring 45. When the car wheel I5 is rotating at a uniform speed, the flexible leaf spring 42 holds the inertia ring 31 in a certain normal position in which the lug 55 is substantially midway between the lugs 56. Upon acceleration or deceleration of the car wheel I5, the inertia ring 31 tends to lag behind or under-speed the car wheel or to overspeed the car wheel respectively and thus shifts rotatively with respect to the car Wheel I5 either backwardly vor forwardly of its normal position a degree corresponding to the rate of acceleration or deceleration of the car wheel, the maximum limit of relative movement of the inertia ring and the car wheel I5 being determined by the engagement of the lug 55 and one or the other of the lugs 56.

As previously indicated, the inner end of the leaf spring 42 is fixed to the tubular member 43. As will be apparent in Figs. 2 and 3, the inner end of the leaf spring is actually held in a metallic channel member 58 which is securely fitted into a recess in an insulating block or base 59 that is in turn secured to the tubular member 43 as by plurality of bolts 6I.

Disposed on one side of the leaf spring 42 are four contact fingers 62, 63, 64 and 65 and on the opposite side of the leaf spring is a single contact finger 66. Each of the contact fingers is in the form of a bell-crank lever pivoted at the fulcrum thereof on va pin 68 of insulating material which is carried byand iixed in the insulating base 59, the contact fingers 62 to 65 being pivoted on the same pin 68 and separated from each other by insulating washer-like spacers 69. Each of the contact fingers is yieldingly urged pivotally toward the leaf spring 42, by a corresponding associated coil spring 1I which acts on one arm of the contact finger. An adjusting screw 'I2 is provided for each Contact finger which is suitably carried by the insulating base 59 and screwed to a position so as to limit or stop the movement of the contact fingers in the direction of the leaf spring under the influence of the spring 1I. The adjusting screws 12 for the contact fingers 62 to 65 are adjusted to different positions so that in the normal position thereof, the contact iin-gers 62 to 65 are spaced successively greater distances away from the leaf spring 42 in the order named. The leaf spring 42 is provided on opposite sides thereof with a plurality of contact discs 13 suitably disposed so as to register with and contact the outer end of corresponding contact fingers 62 to 65. Thus, when the inertia ring 31 shifts rotatively with respect to the car wheel in .one direction from its normal position, the leaf spring 42 successively contacts the co-ntact fingers 62 to 65 and, when the inertia ring 31 is shifted in the opposite direction from its normal position, the leaf spring 42 engages the contact nger 66.

The position of the contact fingers 62 to 66 and the strength of the flexible spring 42 may be such for example that when the car Wheel I5 is rotatively decelerated at a rate corresponding to retardation of the car or train at a rate of 2.75 miles per hour per second, a rate of 3.75 miles per hour per second, a rate of 4.4 miles 'per hour per second and a rate of 5.0 miles per hour per second the leaf spring 42 successively engages the contact fingers 62, 63, 64 and 65, respectively. In a similar manner the position of the contact finger 66 and the strength of the spring 2 may be such that when the car wheel l5 accelerates rotatively at a rate corresponding to a rate of acceleration of the car of 2.75 miles per hour per second, the leaf spring i2 engages the contact finger 66.

As will be made apparent hereinafter, the leaf spring 42 and the contact fingers @2 to 6B accordingly constitute electrical switch means for effecting brake control operations hereinafter to be described. In order to provide a continuous electrical connection to the leaf spring l2 and to contact ngers d2 to se, it is of course necessary to provide collector or slip rings (ii, |32, 83, 84, and 3S corresponding respectively thereto, secured side by side in insulated relation to the inner end of the tubular member 53, as by a plurality of bolts 8l, and concentric to the axle 39.

The slip ring El is connected by a wire E8 to the channel member 58 in which the inner end of the leaf spring l2 is fixed. Each of the contact fingers (S2 to 55 is connected to corresponding slip rings 82 to Sii, respectively, by corresponding wires 852, the connection to the contact lingers being made through a terminal post or strap 9| that is engaged by one end of the coil spring ll biasing the Contact fingers to the normal position thereof.

A suitable brush holder Q2 is provided for holding suitable brushes in Contact with each individual slip ring fil to 86, each individual brush having a wire connected thereto. The brush holder 95: is mounted stationarily in any suitable manner as on a bracket se secured as by screws 15 to a split ring El@ that is securely fastened to the non-rotatable axle 3L, In order to protect and cover the parts of the rotary inertia device iii, a suitable casing 3 may be provided. As shown, such a casing may comprise two substantially semi-circular portions having cooperating flanges adapted to be secured together along a horizontal line at the level of the axis of the axle 39, the two portions of the casing being so formed as to closely surround and be secured at one end to the hub portion 33 of the car wheel l5 as by screws @9 and having an opening mi at the opposite end thereof through which the axle 3Q extends. The wires connected to the brushes of the brush holder 92 may be bound together in a suitable cable H32 which is conducted out of the casing @Si through the end opening Mii.

Slip magnet valve li comprises a casing having a chamber into which one section of the brake cylinder pipe 35 leading from the cut-off magnet valve le is connected7 and a passage lli@ to which the section of the brake cylinder pipe 35 leading from the brake cylinder is connected. Contained in the chamber H33 is a ball valve |535 which is normally unseated from an associated valve seat, formed on the casing, by the fiuted stem Miliof a valve piston l'l which is normally urged upwardly into seated relation on an annular rib seat Iii@ by a coil spring iii@ interposed between the casing and the back side of the valve piston ml. Formed in the casing is a suitable bore in which operates a valve piston hereinafter designated a release valve, that is yieldingly urged into seated relation on an annular rib seat lil, to close an exhaust port H3 opening out of the passage itil, by a coil spring IM interposed between the casing and the back side of the release valve lll.

The slip magnet valve ll further comprises a magnet valve device having a double beat valve Iii and an eleotro'rna'gnet winding that is effective, when energized, to shift the double beat valve from an upper seated position, to which it is normally yieldingly urged by a coil spring |25, to a lower seated position. The double beat valve H6 is effective to control the operation of the valve piston |01 and associated ball valve |05 as well as the release valve in the manner to be hereinafter made apparent. The double beat valve H5 is contained in a chamber lill and in its upper seated position closes an exhaust port ||9 opening out of the chamber l i8 and establishes communication from the passage |04 in the casing to the chambers at the back side of the valve piston |031 and the release valve respectively through a branch passage IBI, passage |22 and a branch passage |23.

With the magnet winding ill deenergized and double beat valve H6 in its upper seated position, iiuid under pressure may be supplied through the brake cylinder pipe 555 past the unseated ball valve H15, through the passage |04 and brake cylinder pipe 35 to the brake cylinder lll without operation of the ball valve m5 or the release valve lll. It will be apparent that such is the case because with the double beat valve l i5 in its upper seated position, fluid under pressure is supplied from the passage |05 to the chamber at the back side of the valve piston |61 and the chamber at the back side of the release valve iii, thus equalizing the pressures on opposite sides of the valve piston and release valve rendering the associated coil springs |09 and l M effective to maintain the valve piston |01 and release valve ill in their normal positions respectively.

With fiuid under pressure being supplied through the brake cylinder pipe 35 to the brake cylinder I4, energization of the magnet winding lll causes the double beat valve H6 to be shifted to its lower seated position in which it cuts off the supply of fluid under pressure from the passage loll to the chambers at the back side of the valve piston |01 and release valve and at the same time exhausts fluid under pressure therefrom through the exhaust port IIS. Thus, due to the unbalancing of the iuid pressures acting on the valve piston |61 and the release valve HI, the valve piston lill is shifted downwardly into seated relation on an annular gasket seat |24 while the release valve III is shifted upwardly into engagement with an annular stop shoulder |25 projecting into the bore in which it operates.

When the valve piston ml is shifted downwardly, the uted stem |636 thereof is withdrawn from supporting relation under the ball valve H35, and the ball valve thus drops into seated relation on an associated seat to cut off and prevent the further supply of fluid under pressure therepast from the chamber |33 to the passage lili. Also, in shifting upwardly the release valve l Il is unseated from its annular rib seat ||2 and accordingly fluid under pressure is exhausted from the passage |04 connected to the brake cylinder through the exhaust port H3. As will be made apparent hereinafter the exhaust port ||3 is a relatively large port so that when the release valve is unseated fluid under pressure is very rapidly vented from the brake cylinder |4.

The chambers at the back side of the valve piston |81 and release valve I|| are connected together through a passage |21 containing a one-way or check valve |28 shown as the ball type that is so arranged as to prevent the flowV of uid under pressure from the chamber at the back side of the release valve to the chamber at the back side of the valve piston |01 but permitting reverse ow of fluid under pressure therepast. The purpose of the passage |21 and check valve |28 is to isolate the chamber at the back side of the valve piston |01 and prevent the supply of iluid under pressure thereto when the magnet winding ||1 is subsequently deenergized. It will be apparent that when the magnet winding ||1 is deenergized, communication is reestablished by the double beat valve ||6 through which '.duid under pressure is supplied from the passage |04 to the chamber at the back side of the release valve Thus, when the magnet winding |I1 is deenergized, the release valve I|| is promptly reseated to close the exhaust port I3. However, since the valve piston |01 is seated on its annular gasket seat |24 and since the ball check valve |28 prevents the supply7 of uid under pressure therepast to the chamber at the back side of the valve piston |01, the uid under pressure eiective on the upper face of the valve piston |01 maintains it in seated position on the annular gasket seat |24 notwithstanding the deenergization of the magnet winding |11. Accordingly, the ball valve |05 is maintained seated to prevent the supply of uid under pressure therepast to the brake cylinder from the brake cylinder pipe 35. The purpose of this operation will be made apparent hereinafter.

rl"he slip magnet valve I1 further comprises an electromagnetically operated switch device which is actuated in response to the energization and deenergization of the magnet winding ||1. As shown in Fig. I, the switch device referred to comprises a contact member |3| which is carried in insulated relation on an armature or stem |32 associated with the magnet winding |I1 and through which operation of the double beat valve ||6 is effected. When the magnet winding |I1 is deenergized, contact member |3| is shifted to a position out of contact with a pair of associated stationary contact members |33. l/Vhen the magnet winding |I1 is energized, the Contact member |3| engages the contact members |33 and thereby establishes a holding circuit for maintaining the magnet winding I|1 energized in the manner to be hereinafter described.

The reapplication magnet valve I8 comprises a casing having a suitable bore containing a valve piston |35, hereinafter referred to as the supply valve, that is operatively controlled by a pliot double beat valve |36 and its associated 0perating magnet winding |31. Supply valve |35 is normally urged downwardly into seated relation on an annular rib seat |38 by a coil spring I 39 interposed between the casing and the back side of the supply valve |35. A branch of the brake cylinder pipe 35 is connected to and opens into a passage that in turns opens within the annular rib seat |38, and the space at the outer seated area of the supply valve is connected by a pipe and passage |4| to the supply reservoir 3|. Supply reservoir 3| is connected to and charged with fluid under pressure from the brake pipe through a branch pipe |42 containing a one-way or check valve |43 to prevent reux of fluid under pressure from the reservoir to the brake pipe. When the supply valve |35 is unseated from the annular rib seat |38, communication is established from the reservoir pipe |4I to the brake cylinder pipe 35 and thus fluid under pressure is supplied from the supply reservoir 3| to the brake cylinder I4. A choke element |44 is provided for suitably controlling the rate of supply of fluid under pressure from the supply reservoir 3| to the brake cylinder I4.

The double beat valve |36 is contained in a chamber |45 that is constantly connected through a passage |46 to the chamber at the back side of the supply valve |35 and, when the double beat valve |36 is in its upper seated position, uid under pressure may be supplied from a branch passage |41 of the passage |4| past the valve to the chamber at the back side of supply valve |35. The double beat valve |36 is normally urged to its upper seated position, in which it closes an exhaust port |48 opening out of the chamber |45, by a coil spring |43 interposed between the valve and the casing.

When the magnet winding |31 is energized, it actuates an armature or plunger |5| to shift the double beat valve |36 to its lower seated position so as to close the supply communication from the passage |41 to the chamber at the back side of the supply valve |35 and at the same time vent fluid under pressure from the chamber through the exhaust port |43. Since the pressure of the fluid in the lsupp-ly reservoir 3| is constantly eiective on the outer seated area of the supply valve |35, the exhaust of fluid under pressureequalizing the pressure on the supply valve to cause the spring |39 to instantly reseat the supply valve on the annular rib seat |38.

It should be understood that the operation of the supply valve |35 in response to the operation of the double beat valve |36 is practically iiistantaneous and, therefore, that the supply valve i |35 is actuated instantly in response to energization and deenergization of the magnet winding The reapplication magnet valve I8 further comprises a switch device including a contactv member |53 carried in insulated relation on the armature I5| associated with the magnet winding |31 and a pair of spaced contact members |54 carried in insulated relation by the casing in the manner not shown. Contact members |53 and |54 are so arranged as to be in contact when the magnet winding |31 is deenergized and that the contact member |53 disengages the contact members |54 in response =to the energization of the magnet winding |31. The switch device formed by the contact members |53 and |54 is connected in series relation with the switch device comprising contact members I 3| and |33 of the slip magnet valve |1 and the purpose of this arrangement urged upwardly into seated position on an annular rib seat |6.| by a coil spring |52 interposed between the casing and the back side of the Valve piston |51, and the uted stem |56 of the valve piston |51 extends through a bore |63 into the chamber |64 containing the ball valve |55 and supports the valve in raised position away from its associated valve seat. The chamber |65 is connected by a section of the brake pipe 35 to the brake cylinder port of the brake controlling valve l2 and the bore |63 is connected by a passage |65 to another section of the brake pipe 35 that leads to the slip magnet Valve H1. rIhus, in the normal positions of the valve piston |51 and the ball Valve |55, iiuid under pressure may be supplied under the control of the brake controlling valve |2 through the brake cylinder pipe 35, past the ball valve |55 of cut-off magnet valve |53 to the section of the brake cylinder pipe 35 leading to the slip magnet valve l1.

The double beat valve |58 is contained in a chamber |66 which is connected through a passage |61 to Ithe chamber at the back side of the valve piston |51. The double beat Valve |58 is normally urged by a coil spring |12 to an upper seated position in which it closes an exhaust port |68 opening out of the chamber |66, and opens a supply port |69 connecting the chamber |68 shift the double beat valve |58 to its lower seated position in which it closes the supply communi- A cation from :the passage |55 to the chamber at the back side of the valve piston |51 and opens the exhaust port |68 to cause fluid under pressure to 'be rapidly exhausted from the chamber at the back side of the Valve piston. With the Venting of fluid under pressure from the chamber at the back side of the Valve piston |51, the uid pressure acting on the upper face of the Valve piston becomes eiTective to over-come lthe spring |62 and shift the Valve piston |51 downwardly to a limit position to cause seating of the ball valve |55, communication between the chamber |66 and chamber at the back side of the valve piston |51 being maintained open through the passage |61. When the magnet winding |59 is deenergized, the spring 1| promptly shifts the double beat valve |58 to its Lipper seated position closing the exhaust port |68 and opening the supply port |69, thereby promptly equalizing the fluid pressures on the valve piston |56 and causing the spring |62 to promptly return the valve piston upwardly to cause unseating of the ball valve |55.

The retardation switch 2l] is illustrative ci any suitable device responsive to the rate of retardation of the car or train. As shown, the retardation switch 26 comprises a casing in which is formed a chamber |15 containing a rolling member, such as the ball |16, which is relatively heavy. Ball |16 is adapted to roll on a smooth surface |11, formed on a wall of the casing, and is conned closely within a slot or opening |18 formed in a member |19 slidably mounted in the casing so as to shift the member |19 correspondingly therewith. A coil spring lill, interposed between the end wall of the casing and a collar or ange |82 on the member |19, yieldingly urges the slidable member and ball in the left-hand direction as seen in Fig. l, the movement of the slidable member |15 in the left-hand direction being limited by the engagement of a shoulder formed thereon with the end wall of the casing. The slidable member |16 carries in insulated relation thereon a contact member |65 which is adapted to engage a pair of spaced stationary contact members |65 that are carried in insulated relation on the casing of the retardation switch in manner not shown, when the sliding member |19 is in its left-hand limit position.

The spring lill is of such strength in relation to the weight oi the ball |16 as to maintain the contact member |665 in engagement with its associated contact members i65 against the inertia force acting on the ball |15 due to the retardation of the car or train as long as the rate of retardation of the car or train does not exceed a certain rate, such as 2.25 miles per hour per second. When the rate of retardation of the car or train exceeds this certain rate, the force of inertia on the ball |16 is eiective to overcome the spring |8| sufficiently to shift the sliding member E16 in the right-hand direction and thereby cause disengagement of the contact member 66 from its associated contact members |85.

The relays 23, 24 and 21 are of conventional design including an electromagnet winding and associated magnetic core with an armature adapted to be actuated in response to the energization to the electromagnet winding. As shown diagrammatically, the relay 23 comprises an electromagnet winding 23a, effective when energized to actuate an armature and cause a contact member 23h carried in insulated relation thereon to engage a pair of stationary contact members 23e, the contact member 23h being biased out of contact with the contact members 25e by gravity or by other biasing means not shown upon deenergization of the magnet winding 23a..

In a similar manner the relay 21 comprises a magnet winding 21a, a contact member 21h carried in insulated relation on the armature actuated by the magnet winding, and a pair of stationary contact members 21e adapted to be engaged by the contact member 21o when the magnet winding 21a is energized and to be disengaged by the contact member 2lb when the magnet winding is deenergized.

In a similar manner also, relay 25 comprises a magnet winding 25d, a pair of contact members Zlib and 24o carried in insulated relation on the armature actuated by the winding, and two pairs of contact members 25d and 25e which are engaged by the contact members Mb and 2de respectively when the winding is energized. The contact members Elib and 25o are separated by gravity or other biasing means not shown from the associated pairs of contact members Zlld and 24e when the magnet winding 24a is deenergized.

'Ihe emergency protection switch 28 is illustrative of any suitable pressure-operated switch. As shown diagrammatically, it may comprise a casing containing a piston E61 having a stem |88 on which is carried in insulated relation a contact member |89 which cooperates with a pair of stationary insulated Contact members ried by the casing in a manner not shown. At one side of the piston |61 is a chamber |52 which is constantly connected by a branch pipe |93 with brake pipe 6|. At the opposite side of the piston |81 is a coil spring |65 which is interposed between the piston and the end wall of the casing in such manner as to be effective to shift the piston and the contact member |89 in a direction to separate the contact member |89 from its associated contact members I9I when the pressure in the brake pipe II and connected chamber |92 of the switch device reduces below a certain low pressure, such as I pounds per square inch.

Since the brake pipe I I is normally charged to a pressure, such as ninety pounds per square inch as previously indicated, the piston |81 is normally shifted downwardly by the pressure of the fluid in the chamber |92 against the force of the spring |94 to effect engagement of the contact member |89 with contact members I9I. Furthermore, due to the fact that the brake pipe pressure is never reduced to or below ten pounds per square inch during a service application of the brakes, contact member |89 of the emergency vprotection switch 2'8 is maintained in contact with its associated contact members I9I during a service application. During an emergency application of the brakes, however, the pressure in the brake pipe is reduced to atmospheric pressure and consequently contact member |89 is actuated out of contact with its associated contact members |9| only during an emergency application of the brakes. The purpose of the emergency protection switch 28 will be made apparent hereinafter.

The pressure switch 33 is similar in construction to the emergency protection switch 28 and therefore it is deemed unnecessary to describe its construction except to point out that corresponding parts in the two pressure switches are designated by the same reference numerals. The chamber |92 of the pressure switch 33 is connected by a branch pipe |96 to the brake cylinder pipe 35 at a point between the cut-off magnet valve I9 and the brake controlling valve I2 and is thus operated in response to the pressure of the fluid supplied to the brake cylinder I4. The coil spring |94 of the pressure switch 33 differs in strength from that of the spring I 94 of the emergency protection switch 28 in that it permits movement of the piston to effect engagement of the contact member |89 with its associated contact members I 9| when the pressure in the brake cylinder pipe 35 eX- ceeds a pressure such as ve pounds per square inch. It will thus be apparent that substantially at the time that the application of the brakes is initiated, Contact member of the pressure 33 is actuated into contact with its associated contact members I9I.

One of the contact members I9I of the pressure switch 33 is connected to one of the terminals, hereinafter referred to as the positive terminal, of the battery 32 by a wire |91 and the other contact member I 9| has connected thereto a wire |93, hereinafter referred to as the battery wire. It will thus be seen when the contact member |39 of switch 33 engages its contact members I 9|, battery wire I 93 is `connected to the positive terminal of the battery 32; and also that unless the contact member |89 does engage its contact members I9I, the supply of current from the battery 32 to the battery wire |93 is prevented. The purpose of this feature will be made apparent hereinafter.

Various electrical circuits are provided for effecting operation and control of the parts of the equipment above described. It is deemed unnecessary to specifically describe these circuits at this time, since they will be described in detail hereinafter in connection with an assumed operation of the equipment.

OPERATION or EQUIPMENT (a) Service application of the brakes Let it be assumed that the brake pipe II is charged to the normal pressure carried therein, say ninety pounds per square inch, so that the supply reservoir 3! is correspondingly charged, the emergency protection switch 23 is in its closed position and the brake controlling valve device i2 conditioned in its release position to vent fiuid under pressure from the brake cylinder I4 through the brake cylinder pipe 35 and exhaust port of the brake controlling valve I2, the auxiliary reservoir I3 being at the same time charged to the pressure of the brake pipe. Let it be further assumed that the car or train of cars is travelling along the road at a substantially uniform speed, either under power or coasting, so that the inertia ring 3l of the rotary inertia device it associated with the car wheel I5 and also the inertia ring of the other rotary inertia devices associated with all the other wheels of the car or train are in the normal position thereof with respect to the associated wheels. With the car or train traveling at a uniform speed as assumed, the ball of the retardation switch 29 has substantially no inertia forces acting thereon and consequently contact member |35 of the retardation switch is in contact with its associated contact members |85, as shown. Furthermore, since the pressure in the brake cylinder pipe 35 is at atmospheric pressure, the pressure switch 33 is in open position, as shown.

As will be made apparent hereinafter, the slip magnet Valve I?, the reapplication magnet valve IB, the cut-off magnet valve I9 and the relays Z3, 24 and 2l are correspondingly conditioned as shown in Fig. 1.

Now let it be assumed that the operator desires to effect la service application of the brakes and. after iirst cutting off the propulsion power if the power is on, effects a reduction in the pressure in the brake pipe II at a service rate and to an amount corresponding to the desired degree of the service application of the brakes.

The brake controlling valve I2 accordingly operates in response to the reduction of the pres` sure in, the brake pipe I I at a service rate to cause fluid under pressure to be supplied fromf the auxiliary reservoir I3 into the brake cylinder pipe 35 and then serially through pipe 35 past the unseated ball valve |55 of the cut-off magnet valve I9 `and the unseated ball valve |05 of the slip magnet valve I'I to the brake cylinder I4 associated with the car Wheel I5, to effect application of the brakes thereon. It will be understood that the supply of uid under pressure to the brake cylinder I 4, or to a plurality of parallel connected brake cylinders, effects application of the brakes on all of the wheels of the wheel truck having the car wheel I5. In a similar manner, it should be understood that nuid under pressure supplied into the brake cylinder pipe 35 also ows through a branch pipe of the brake cylinder pipe to one or more brake cylinders `associated with the car wheels of the Wheel truck at the opposite end of a car, to effect application of the brakes thereon.

ihen the pressure in the auxiliary reservoir I3 is reduced by flow to the brake cylinders an amount corresponding to the amount of reduction in brake pipe pressure, the brake control- CJI ling valve I2 is operated in conventional manner to lap position to cut oi the further supply of iiuid under pressure from the auxiliary reservoir I3 to the bra-ke cylinders so that the degree of pressure established in the brake cylinders corresponds to the amount of the reduction in brake pipe pressure.

Let it be assumed for example that the pressure established in the brake cylinders is twentyve pounds per square inch. Thus, since the pressure in the brake cylinder pipe 35 is in excess of five pounds per square inch, the pressure switch is operated to closed position connecting positive terminal of the 'battery S2 to the battery wire ISB. Since, as previously explained, the rate of retardation of the car or train is not sufcient to cause opening of the retardation switch 2B, closure of the pressure switch 33 establishes a circuit for energizing the relay 2l, this circuit extending from the battery wire ISS through a branch wire ESI, contact members |35 and IM of the retardation switch 2li, a wire 2&22, retardation wire 22, a branch wire m3, inagnet winding 2M of relay 2l to the negative terminal of the battery 32 as through a ground connection in the manner indicated. Contact member 2lb of relay 21 is accordingly actuated into engagement with its associated contact members 21C, which operation is without eect, however, unless the car wheel I5 or any of the car wheels of the same truck begin to slip. If none of the car wheels of the wheel truck having the wheel I5 slip, then no operation of the equipment occurs as a result of operation of relay 2'I, and the degree of the application of the brakes continues under the control of the operator in the conventional manner of automatic air brake equipment.

1f the car wheel l5 begins to slip, however, due to the application of the brakes exceeding the adhesion between the wheel and the associated rlaii, then, due :to the increase in the rate of rotative deceleration Iof the car wheel It, the inertia ring 31 of the rotary inertia device I6 associated with the wheel I5 begins to shift relative to wheel l5 in a clockwise direction as seen in Fig. l, assuming that the motion of the car or train is in the right-hand direct-ion as indicated by the arrow above the wheel i5. When the rate of rotative deceleration of .the car wheel I5 exceeds the rate corresponding to a rate of retardation of the car of 2.75 miles per hour per second, the leaf spring 42 engages the conta-et finger 62 and a circuit is thereby completed for energizing the magnet winding M7 of the slip magnet Valve Il. This circuit extends from the battery Wir-e Hi8 through a branch wire 235 having in series relation therein an inductance or choke coil 252B the purpose of which will be presently explained, leaf spring (l2, Contact linger 62, a wire 2li?, contact members 2lb and 21C of relay 2l, a wire 268, Contact members I9! and H39 of the emergency protection switch 28, a wir-e 209, magnet winding [Il of the f slip magnet valve I1," and balck to the negative terminal of the battery 32 as through a ground connection in the manner shown. The inductance coil 2% momentarily delays the flow of current through the energizing circuit .just describe-d so :as to prevent energization of lthe magnet winding I I'I if the leaf spring E42 accidentally engages the Contact finger 62 due to shock or jar to the cars. The provision of the choke coil 266 in the manner and for the purpose disclosed herein has been previously disclosed and claimed in my prior pen-ding yapplication Serial No. 248,654, previously menticned.

Upon the energization of the magnet winding Il 'l of the slip magnet valve il, the contact member ll is actuated into contact with its associated contact members to establish a holding circuit for maintaining the magnet winding III".l energized thereafter until such time as the holding circuit is interrupted in the manner to be hereinafter described. r'he holding circuit exends from the battery wire through Contact members loll and l or" the reapplic'a'tion magnet valve i3, a wire 2id, contact members i3d and lil! of the slip magnet valve il, magnet winding l il and back to the negative terminal oi the baittery through the ground connection indicated. The purpose of the holding circuit will be made apparent presently.

As previously described in connection with the description oi the slip magnet valve il, the enerthe release Valve lili to be uns-cated and vent L.

fluid under pressure from the brake cylinder I4 through the exhaust port Ill at a rapid rate. Accordingly the brakes `associ-ated with all of the wheels of the wheel truck having the Wheel i5 are correspondingly released even though the 'fl' other wheels may not have begun to slip. The reason for releasing the brakes on all the wheels of a given truck simultaneously is that if one wheel begins to sli-p all the others may be danger- -ously close to the slipping point and consequently the instantaneous release oi the .brakes therefrom prevents the wheels from slipping.

Due to the rap-id release of fluid under pressure from the brake cylinder it under the control oi' the slip magnet valve il, the slipping wheel I5 does not decelerate to a locked-wheel or sliding condition but begins to, accelerate back toward a speed corresponding to vehicle speed. The car wheel lli laccordingly ten-'ds to overspeed the inertia ring 3l of the associated rotary inertia device Ii and the inertia ring il accordingly shiilts backwardly `of its normal position an amount corresponding to the rate of rotative acceleration of the car wheel I5. The rate of rotative acceleration of a slipping car wheel back tov/ard car speed is at least equal to if not greater than the rate oi rotative deceleration of the wheel while slipping and, consequently, the engagement of the le'af spring 42 of the notary inertia device with its associated Contact iin-ger lili is eifccted, it being |recalled that any rate of rotative acceleration in excess olf 2.75 miles per `hour per second is sufficient to cause the leaf spring to engage the contact nger iifa.

Upon the engagement of the leaf spring 42 with its Contact finger 65, a circuit is completed for energizing the magnet winding I3? of the reapplication magnet valve i3, this circuit extending from the battery wire ISB to the leaf spring l2 as previously described, then -by way of the Contact finger 56, a wire 2l I, magnet winding lil? ot the rea-pplioation magnet valve ill and back to the negative terminal cf the battery 32 as through a grou-nd connection in the manner sllown. As previously described in connection with the reapplicatio-n magnet valve I3, the energiaation of the magnet winding 31 thereof effects operation of the supply valve F35 "to supply uid under pressure from the supply reservoir SI tio the brake cylinder Il and, at the same time, actuation of the Contact member |53 out of engagement with its associated contact finger members |54. The separation o-f the contact member |53 from contact members I54 interrupts the holding circuit of the magnet winding II'I of the slip magnet valve I'I, which is accordingly deenergized. The release valve III 'of the slip magnet valve I'I is thus promptly returned to seated position cutting off the further exhaust of fluid under pressure from the brake cylinder I4 through the exhlaust port I I3 substantially at the instant that the supply valve |35 of the reapplication magnet valve is unsealted to supply fluid under pressure from tfhe brake cylinder. Fluid under pressure is resupplied to the brake cylinder I4 at a rat-e determined by the flow area of the choke element |44 so that the pressure in the brake cylinder |4 is restored at a controlled rate.

It will be observed, as previously indicated, that notwithstanding deenergization of magnet winding IfI 'I, .the valve piston IUI is maintained in its lower position so that the ball valve |05 is consequenitly maintained effective to prevent the further supply of fluid under pressure from the auxiliary reservoir I3 through the brake cylinder pipe 35 to the :brake cylinder I'4. The reason for maintaining the b-all valve |05 in its seated -position is to prevent the reduction of the pressure in the brake cylinders associated with 'the other wheel -truck or trucks on the car by flow through the brake cylinder pipe 35 thus lreducing the degree o'f application of the brakes associated with the other truck or trucks o-n which a wheel may noit have slipped.

When the slipping car wheel I5 approaches car speed, the rate of rotative acceleration thereof decreases sufficiently to effect separation of the leaf spring 42 from the associated contact finger 66 of the rotary inertia device I6 and the circuit for energizing the magnet winding |31 of the reapplication magnet valve I8 is correspondingly interrupted. The supply valve |35 of the reapplication magnet valve I8 is thus instantly reseated to prevent the further supply of fluid under pressure from the supply reservoir 3| to the brake cylinder I4 in response to the deenergization of the magnet winding |3'I, and contact member |53 of the reapplication magnet valve is returned into contact with its associated contact members |54. Since the contact member |3| of the slip magnet valve I'I is disengaged from its associated contact members |33 upon deenergization of the magnet winding III, the reengagement of the contact member |53 with its contact members |54 does not effect reenergzation of the magnet winding III.

It will thus be apparent that fluid under pressure is resupplied to the brake cylinders I4 from the supply reservoir 3| only as long as the rate of rotative acceleration of the slipping wheel I5 exceeds a rate such as 2.75 miles per hour per second in returning back toward car speed. The time that the car wheel I5 exceeds the rate of rotative acceleration of 2.75 miles per hour per second is sufliciently short and the size of the choke element |44 is suitably designed that the pressure restored in the brake cylinder I4 will not be suicient to cause the Wheels to again begin to slip. However, if for some reason, such as a change in the adhesion of the car Wheels to the track rail, the wheel I5 should again begin to slip,

the release valve I I I of the slip magnet valve I'I is again operated to rapidly reduce the pressure in the brake cylinder and the reapplication magnet valve I8 is subsequently operated to resupply pressure to the brake cylinder so that at no time is the car wheel i5 permitted to attain a locked- Wheel or sliding state due to slipping.

It should be noted, however, that if for some reason or other the car Wheel I5 should actually decelerate to a locked-wheel condition and slide, it can slide only momentarily because the release valve III of the slip magnet valve II'I is maintained in exhaust position until the slipping Wheel positively accelerates at a rate in excess of 2.75 miles per hour per second. Thus, release of the fluid under pressure from the brake cylinder I4 is continued as long as necessary to assure the restoration of a slipping car wheel to a rolling state and prevent it from sliding more than momentarily, if at all.

(b) Release of brakes following service application When the car or train has been brought to a complete stop by a service application of the brakes and the operator desires to release the brakes prior to again starting the car or train, he may release the brakes merely by restoring the pressure in the brake pipe II to its normal pressure. The brake controlling valve I2 accordingly operates in response to the restoration of the normal pressure in the brake pipe to Vent fluid under pressure from the brake cylinder pipe 35 through the exhaust port thereof and, at the same time, to recharge the auxiliary reservoir I3 to the pressure carried in the brake pipe.

It willvbe apparent that the ball Valve |05 of the slip magnet valve II unseats upward in response to the exhaust of fluid under pressure from the brake cylinder pipe 35 to permit the exhaust of fluid under pressure from the brake cylinder I4 through brake cylinder pipe 35 to atmosphere at the brake controlling valve I2. When the pressure acting on the upper face of the valve piston IIl'I of the slip magnet valve II reduces to a relatively low pressure, such as live pounds per square inch, the spring |09 becomes eiTective to shift the valve piston Ill'I upwardly to its normal position in which the stem |36 of the valve piston holds the ball valve |05 unseated in its normal position, thus restoring the slip magnet valve I1 to its normal condition.

When the pressure in the brake cylinder pipe 35 reduces below the low pressure such as iive pounds per square inch, the pressure switch 33 is likewise shifted to its open position disconnecting the battery wire |98 from the positive terminal of the battery 32, thereby interrupting the circuit for energizing the magnet winding 27a of the relay 2'I and causing the contact member 2lb thereof to be shifted to its open position.

(c) Emergency application of the brakes Let it now be assumed that with'the brakes released and the equipment conditioned as shown in Fig. 1, and the train of cars traveling along the road under power at a substantially uniform high speed, the operator desires to effect an emergency application of the brakes. To effect an emergency application of the brakes, the operator first cuts off the propulsion power, if this power is on, and then effects a reduction of pressure in the brake pipe II at an emergency rate in the usual manner. The brake controlling valve I2 accordingly operates in response to the emergency reduction of pressure in the brake pipe to supply uid under pressure from the auxiliary reservoir I3 through the brake cylinder pipe 35 to the brake cylinder I4 at an emergency rate.

When the pressure switch 33 closes, contact member y2lb of relay 2'I is actuated to closed position but is immediately returned to open position due to the opening of the retardation switch 2l) when the rate of retardation of the car or train exceeds the rate of 2.25 miles per hour per second. Since the car or train is traveling at a high speed, the application of the brakes to a degree sufficient to cause a rate of retardation in excess of 2.25 miles per hour per second will be insufcient to cause slipping of the car Wheel I5 and consequently the momentary closure of the contact member 2lb of relay 21 is Without effect since the leaf spring 42 of inertia device IB associated with the car Wheel I5 is not actuated into conltact with the contact iingler 2 before relay 2l is returned to its open position.

The emergency protection switch 23 is actuated to open position promptly in response to the emergency reduction of pressure in the brake pipe I I and thus interrupts the circuit, previously traced, for energizing the magnet Winding II'I of slip magnet vvalve H. .Accordingly undesired operation of the slip magnet valve to exhaust uid under pressure from the brake cylinder I4 is prevented, should the relay 21 accidentally fail to open before the car Wheels atta-in a rate of rotative deceleration corresponding to a car retardationof 2.75 miles per hour per second.

Accordingly, due to the emergency application of the brakes, the car Wheels I5 continue to decelerate at an increasing rate, Without any automatic control of .the brake cylinder pressure, until the car or train .attains a rate of retardation of 4.4 .miles per hour per second, at Which time the leaf spring 42 of each rotary inertia device i6 engages itsassociated contact finger 64. As Will be made apparent presently, the prior engagement of the leaf spring 42 with its associated contact vfinger 63 is without immediate effect. Upon the engagement -of the leaf spring 42 with its associated contact linger 64, a circuit is completed for energizing `the magnet winding 23a of the relay 23 on every car throughout the train, this circuit extending from the battery Wire |98 to the leaf spring 42, thence by Way of the contact finger 64, a Wire ZIE, synchronizing train Wire 2|, branch Wire 2I6 on each car, magnet winding 23a of relay 23 on each car, and to the negative terminal of ,the battery 32 as through a ground Vconnection in the manner shown.

By` the time that any Wheel of the car or train. assumed in the present instance to be the car Wheel I5, attains a rate of rotative deceleration corresponding to a train retardation of 4.4 miles per hour per second, all other Wheels of the car or train Will have attained at least a rate of rotative deceleration corresponding to a car retardation of 3.75 miles per hour per second sufficient to erfect the engagement of leaf spring 42 of each inertia device I5 With its associated contact finger t3. Accordingly, When the relay 23 on a car is energized due to energization of the synchronizing train Wire 2l, the actuation of the contact member 23D thereof to closed position completes a circuit for energizing the magnet Winding 24a of the so-called stick relay 24. This circuit extends (see Fig. l) from the battery Wire ISES on the car to the leaf spring 42 of every rotary inertia vdevice It as previously traced, thence by Way of the Contact nger 63, a Wire 2 I 8, contact members 23C and 23D of relay 23, a Wire 219, branch Wire 22l, magnet Winding 24a, and

L, to the negative terminal of the battery 32 on the corresponding car as through a ground conm nection in the manner shown in Fig. 1.

The actuation of the contact member 24h of relay 24 on each car into closed position in response to the energization of the magnet winding 24a establishes a holding circuit for maintaining the magnet Winding 24a energized thereafter independently of the corresponding relay 23, the circuit extending from battery Wire I98 through the rotary inertia device I6 to the Wire ZIB as previously traced, thence by a branch Wire 222, Contact members 24d and 24h of relay 24, Wires 2 I9 and 22 I magnet winding 24a and to the negative terminal of the battery 32 through the ground connection shown.

The engagement of the contact member 24o With its associated contact members 24e in response to energization of the magnet Winding 24a of relay 24 completes a circuit for energizing the magnet winding |59 of the cut-off magnet valve I9. This circuit extends from the battery Wire |98 through a branch Wire 223, Contact members 24e and 24C, a Wire 224, magnet Winding 59 of the cut-off magnet valve I9 and to the negative terminal of the battery 32 through the ground connection indicated.

As previously explained in connection with the description of the cut-off magnet valve I9, the energization of the magnet Winding I 59 causes the ball valve to be seated and prevent the further supply of fluid under pressure therepast to the brake cylinder I4 through the brake cylinder pipe 35.

It should be understood that, as indicated in Fig. 1, all the rotary inertia devices I6 on the car or train are so connected that when any wheel of the car or train rst reaches a rate of rotative deceleration corresponding to a car retardation of 4.4 miles per hour per second, the synchronizing train Wire 2I is energized just as described in connection with `the rotary inertia device Il associated Withthe car Wheel I5. Accordingly, Whenever any Wheel on the car or train attains a rate of rotative deceleration corresponding to a car retardation of 4.4 miles' per hour per second, the ball valve 155 of the cutorf magnet'valve I9 on each car is actuated to seated position to prevent the further supply of' fluid under pressure to the brake cylinders on the corresponding car.

As previously explained, my present brake control equipment is adapted to be employed particularly in connection With wheel brake devices the rubbing parts of which have a so-called friction fading characteristic that results in a reduction of the coeflicient of friction thereof with the continued application of the brakes. Thus, since further increase of the pressure in the brake cylinders AI4 on each and every car is prevented due to the seating of the ball valve |55 of the cut-'off magnet valve I9 on each car, no car Wheel can thereafter decelerate rotatively at a rate in excess of one corresponding to the car rate of retardation of 4.4 miles per hour per second, unless the Wheel slips'. Assuming however that none of the Wheels begin to slip, the brake application Will'be continued at a degree determined by the then attained brake cylinder pressure, diminishing accordingly as the coefcient of friction of the rubbing `parts of the brake devices diminishes due to the friction-fading characteristic of the rubbing parts of the brake devices.

When the `rate of rotative retardation of the car Wheels decreases from the attained maximum of 4.4 miles per hour per second, suniciently that the leaf spring 42 of the rotary inertia device I6 associated with every car wheel disengages its corresponding contact finger 64, the synchronizing train Wire 2I is deenergized and consequently the so-called synchronizing relay 23 on every car is deenergized. As previously indicated, however, the relay 24 has established its own holding circuit and continues to remain energized independently of the deenergization of the relay 23 as long as the rate of rotative deceleration of the car Wheels on the corresponding car exceeds a rate corresponding to car retardation of 3.75 miles per hour per second.

The rotary inertia devices I6 of the car wheels on each individual car are so connected in parallel relation that as long as the leaf spring 42 of any of the rotary inertia devices on the same car engages its corresponding contact iinger 63, the relay 24 for that car remains energized. Thus, upon the separation of the leaf spring 42 of the rotary inertia device I6 associated with the last car Wheel to decrease below a rate of rotative deceleration of 3.75 miles per hour per second, the circuit for energizing the relay 24 is interrupted and consequently the contact members 24b and 24o thereof are restored to open position. The opening of the contact member 24h interrupts the holding circuit for the relay 24, thereby again necessitating a rotative deceleration of a car Wheel on that car at a rate corresponding to a car rate of retardation of 4.4 miles per hour per second before relay 24 can be again energized. The opening of the contact member 24o interrupts the circuit for energizing the magnet winding 159 of the cut-off magnet valve I9, This results in the operation of the valve piston |51 to unseat the ball valve |55 to permit the further supply of fluid under pressure through the brake cylinder pipe to the brake cylinder I4 to further increase the pressure in the brake cylinders on the car and thereby compensate for the decreased braking effort caused by the friction-fading characteristic of the wheel brake devices.

When the car Wheels again begin to decelerate rotatively at a rate in excess of a car retardation of 4.4 miles per hour per second, the relay 24 is again energized to cause operation of the cut-off magnet valve I9. This operation is repeated as often as it is necessary during any one application of the brakes to compensate for the decrease in braking eifort caused by the friction-fading characteristic of the wheel brake devices. Ac-

cordingly, it will be seen that the cut-off magnet valves I 9 on every car are automatically controlled by the rotary inertia devices I6 of any of the car Wheels throughout the train as Well as by any of the rotary inertia devices on the correspending car to limit and regulate the pressure in the brake cylinder so that a substantially uniform rate of retardation of the car or train is effected It will be apparent that since the cut-olf magnet valves I9 are operated when the car wheels attain a rate of rotative deceleration corresponding to a car retardation of 4.4 miles per lour per second, the average rate of retardation of the car or train will be somewhere between the 3.75 miles per hour per second and the 4.4 miles per hour per second which are the lower and upper limits established by the rotary inertia devices.

It should now be apparent that if an individual car Wheel such as the car wheel I5, begins to decelerate rotatively at a rate corresponding to car retardation in excess of the upper lnit of 4.4

miles per hour per second, this is an indication that the wheel is beginning to slip. Thus, if during the application of the brakes, an individual car Wheel I5 should begin to decelerate rotatively at a car rate of retardation of 5 miles per hour per second, the leaf spring 42 of the associated rotary inertia device I6 engages the Contact member 65 and thereby completes a circuit for energizing the magnet winding I I 'I of the slip magnet valve I'I. The slip magnet valve I1 is thus operated, as previously described for a service application of the brakes, to cut off the further supply of uid under pressure through the brake cylinder pipe 35 to the brake cylinder I4 and rapidly vent fluid under pressure from the brake cylinder or cylinders applying the brakes on the Wheel truck having the slipping wheel, In a similar manner also to that described for a service application, the subsequent rotative acceleration of the wheels back toward car speed in response to the release of the brakes and the consequent engagement of leaf spring 42 of the associated rotary inertia device I6 With its contact finger 66 effects operation of the reapplication magnet valve I8 to resupply fluid under pressure to the brake cylinder I4 from the supply reservoir 3l.

It will be apparent that, if an individual car wheel on a particular car begins to slip before the car wheels of other cars have attained a rate of rotative deceleration in excess of 3.75 miles per hour per second, then the energization of the synchronizing train wire 2| due to the engagement of the leaf spring 42 with the Contact finger 64 of the rotary inertia device associated With the slipping Wheel will result in the energization of the synchronizing relay 23 on all cars; but no operation of the cut-off magnet valve I9 on any car other than the car having the slipping wheel will occur because it is necessary for the leaf spring 42 of at least one rotary inertia device on each car to engage its associated contact finger 63 before the relay 24 can be energized to cause operation of the cut-off magnet valve I 9 on that car. Thus, uid under pressure continues to be supplied during an emergency application to the brake cylinders on cars having no slipping Wheels until at least a rate of retardation of the Wheels on the car corresponding to a car retardation of 3.75 miles per hour per second is attained notwithstanding that a wheel may have slipped on another car prior to that time,

After a slipping wheel returns to a rotative speed corresponding to car speed, the pressure reestablished in the brake cylinder I4 associated with that wheel and the other Wheels of the same r wheel truck will not be further increased during the duration of the application of the brakes, for the reason that the ball valve |05 of the slip magnet valve Il remains seated to prevent the supply of iiuid under pressure through the brake cylinder pipe 35 to the brake cylinder. In the event that slipping of a particular wheel again occurs, the slip magnet valve I'I and the reapplication magnet valve I8 associated therewith are again operated in sequence in the manner previously described.

It should be understood that the particular rates of car retardation referred to herein at which the leaf spring 42 of a rotary inertia device engages the associated contact fingers 62 to 66, are purely illustrative. Thus, it should be understood that the regulation of the rate of rotative retardation of the car Wheels to a rate between the lower and upper limits of 3.75 and 4.4 miles per hour per second is merely illustrative of the maximum rate of rotative retardation of a car wheel that can be effected within the limit of the adhesion between the car wheels and the track rails.

if the adhesion between the car Wheels and the track rails is relatively high, then slipping of the car wheels should not occur because the braking force on the car wheels is limited to a value so as not to exceed the limit of the adhesions between the wheel and the rail.

If the adhesion between the car 'wheels and the rails is relatively low, then the car wheels may slip since the braking force may be such as to exceed the adhesion between the car wheels and the rails. However, in such case the rotary inertia devices l function to prevent actual sliding cf the car wheels.

It will thus be apparent that the rotary inertia devices I6 function to control the cut-oilc magnet valves i@ on the cars in such manner as to regulate the pressure in the brake cylinders to a degree so as to produce a maximum rate of retardation consistent with the adhesion between the car wheels and the rails. Since a relatively high adhesion between the car wheels and the rails can be dependably realized a major portion of the time, it will be apparent that the brake control equipment functions to bring a car or train to a complete stop from a high speed in as short a stopping distance as is possible without 'the employment of extraneous or oif-the-wheel brake devices such as track brake devices.

After a car or train has been brought to a complete stop, the inertia ring 3l of each rotary inertia device I6 is restored to its normal position and accordingly the leaf spring 42 thereof disengages all of its associated contact ngers 62 to 65. Thus, due to the separation of the leaf spring 42 from the contact fingers 63 and 64, the cut-oli magnet valve I9 on every car is automatically restored to its normal position in which the ball valve |55 is held unseated. If the supply pressure delivered to the out-oli valve I9 under the control of the brake controlling valve i2 is still in excessof the attained pressure in the brake cylinder, the pressure in the brake cylinder will accordingly build up to a maximum pressure of equalization with the pressure in the auxiliary reservoir i3. In the case of wheel trucks having wheels which slipped during the application, the ball valve |95 of the slip magnet Il remains seated and thus the pressure in the brake cylinders for such wheel trucks is not automatically built up to a maximum pressure of equalization when the car or train comes to a stop.

When a car or train comes to a complete stop, the retardation switch 2U is returned to its closed position and, since the pressure switch 33 is closed, the .circuit is again completed for energizing relay 2l to cause its contact member 2lb to be actuated to close position. The emergency protection switch 28 is in open position, however, and thus the magnet winding l il of the slip magnet valve il cannot be energized as a result of closure of relay 2l. Consequently, the pressure restored in the brake cylinder lf3 by operation of the reapplication magnet valve I3 is retained therein when the car or train comes to a stop.

(d) Release of the brakes following emergency application of the brakes' To effect a release of the brakes following an emergency application of the brakes and prior to again starting the car or train, the operator restores the pressure in the brake pipe Il to its normal pressure by operation of the manually operated brake valve (not shown) in well understood manner. The brake controlling valve l2 operates in response to the restoration of the normal pressure in the brake pipe I to recharge auxiliary reservoir I3 andeXhaust iiuid under pressure from the brake cylinder M through the brake cylinder pipe 35 and to atmo-sphere at the brake controlling valve, in the same manner as previously described for a release following a service application of the brakes.

MODIFICATION SHOWN IN Frs. 4

Referring to Fig. 4, a cut-oil magnet valve E9e is shown which differs from cut-off magnet valve i9 in having a restricted port 250 connecting the chamber E64 and the passage |65 in bypassing relation to the ball valve |55.

When employing cut-olf magnet valve I 9a, fluid under pressure is supplied at a restricted rate to the brake cylinders of a corresponding car when the ball valve |55 of the cut-olf magnet valve ida is seated. Thus, instead of cutting oi the supply to the brake cylinders altogether when the rate of rotative deceleration of the car wheels exceeds 4.4 miles per hour per second and permitting them to thereafter reduce to 3.75 miles per hour per second before resupplying fluid under pressure to the brake cylinders, the restricted port 25S enables a continued restricted ow to the brake cylinder so as to maintain a higher average rate of retardation of the wheels Within the lower and upper limits of 3.75 and 4.4 miles per hour per second determined by the rotary inertia devices I5.

The size of the restricted port 725i: is determined according to the rate at which the coecient of friction of the rubbing parts of the wheel brake devices fades so as to compensate for the reduction in the braking force due to the reduction of the coeilicient of friction.

It should be apparent that where the rate of fading of the coefficient of friction is not uniform and is erratic in its variation, the provision of cut-ofi magnet valves lSa is not desirable because in such case whether or not the friction fading occurs, fluid under pressure will be continuously supplied at a restricted rate through the port 250 of the cut-olf magnet valve thus increasing the likeiihood of slipping of the car wheels.

SUMMARY summarizing, it will be seen that I have provided a brake control equipment for vehicles such as railway cars and trains employing wheel brake devices wherein the rubbing parts of the brake devices possess a friction-fading characteristic, as distinguished from the usual friction-increasing characteristic.

The brake control equipment includes suitable brake cylinders for applying the brakes to the wheels and a conventional pneumatic equipment for controlling the supply and release of fluid under pressure to and from the brake cylinders. According to my invention, a rotary inertia device is associated with each individually mounted and rotatable wheel and is operatively responsive in accordance with the rate of rotative deceleration or acceleration of the corresponding wheel. A retardation switch is also provided which is operative in response to the rate of retardation of the car or train.

During va service application of the brakes, the retardation switch is always so conditioned, due to the fact that the retardation of the car or train never exceeds a certain rate during a service application, as to render the rotary inertia devices associated with the individual car wheels effective when any one wheel of a truck begins to decelerate rotatively at a rate slightly greater than a certain low rate of train retardation to rapidly release fluid under pressure from the brake cylinders applying the brakes on a wheel truck on which a wheel slips and then to resupply fluid under pressure automatically to those brake cylinders to reapply the brakes, in response to the positive acceleration of the slipping car wheel or Wheels back toward car speed.

During an emergency application of the brakes, the retardation switch is conditioned in response to the higher rate of retardation of the car or train to render the rotary inertia devices ineffective at the lower rate of rotative retardation of the car wheels eifective during a service application but effective at a higher rate of rotative retardation to rapidly release uid under pressure from the brake cylinders on the truck having the slipping wheel or wheels and then to automatically resupply iiuid under pressure to those brake cylinders upon positive acceleration of the slipping car Wheels back toward car speed.

The rotary inertia devices associated with the individual wheels are furthermore adapted to so control a cut-olf magnet valve device controlling the supply of fluid under pressure to the brake cylinders during an emergency application of the brakes as to limit the normal rate of retardation of non-slipping car wheels to some rate between an upper and a lower limit so selected as not to exceed the adhesion between the car Wheels and the track rails. The rate at which the rotary inertia devices recognize slipping of wheels during an emergency application of the brakes is slightly in excess of the rate of rotative retardation to which the wheels are normally limited.

It will thus be apparent that the brake control equipment of my present invention is based on the novel principle that rotative deceleration of the car wheels at a rate in excess of the car or train retardation is indicative of a slipping condition thereof.

It will be seen that individually rotatable car wheels will decelerate at a very fast rate once it begins to slip and will attain a locked-Wheel or sliding condition unless the rotary inertia devices respond quickly enough so as to relieve the brake cylinder pressure and thus release the brakes sufficiently rapidly to start the wheel accelerating back toward car speed prior to attaining the locked-wheel condition. By providing an arrangement in which the rotary inertia devices operate to release and reapply the brakes at different rates of rotative retardation of the car wheels depending upon the rate of retardation of the car or train, the requisite sensitivity to the initiation of slip of the car wheels is obtained.

It should be understood that the brake control arrangement including the rotary inertia devices I6, slip magnet valve l1, reapplication magnet valve I8 and retardation switch 2i), may be employed with any type of wheel brake device whether of the friction-fading type or frictionincreasing type.

In regulating the rate of retardation of the car or train during an emergency application of the brakes, the rotary inertia devices function to cause cut-off of the supply of fluid under pressure to the brake cylinders for operating wheel brakes having the .friction-fading characteristic at a point as high as possible consistent with the adhesion between the car wheels and the track rails and then maintain the supply cut off until, dueto the friction-fading, the rate of retardation of the car or train reduces below a lower limit, whereupon fluid under pressure is resupplied to the brake cylinder to compensate for the friction-fading.

A modified cut-off magnet valve is disclosed wherein the supply of fluid under pressure to the brake cylinder is not cut off altogether at the upper limit of retardation determined by the rotary inertia devices but continues to be supplied at a restricted rate designed to compensate for the friction-fading and thus maintain a higher average rate of retardation. If the friction-fading characteristic is not such as to reduce at a uniform rate and is erratic, this modified cut-off magnet valve should not be used since it is apt to result in excessive wheel slipping.

It will be apparent that the brake control equipment disclosed herein is not limited to cars or trains having individually rotatable wheels but may be employed as well on cars of the more conventional type having a unit assembly of a pair of Wheels fixed to an axle. In this case, only one rotary inertia device is required per pair of wheels since the two wheels engaging the opposite rails rotate together. Furthermore, if desired, other types of rotary inertia devices I6 associated with the car wheels or with the axles of the rotatable type may be employed as long as they are adapted to perform the functions of the rotary inertia devices disclosed herein.

' While I have illustrated and described a specific embodiment of my invention, it should be ap.

parent that various omissions, additions or modifications may be made therein without departing from the spirit of my invention. It is accordingly not my intention to limit the scope of my invention except as it is necessitated by the scope of the prior art.

Having now described my invention, what I claim as new and desire to secure by Letters Patent, is:

1. A vehicle brake control equipment comprising means for effecting application and release of the brakes on the vehicle, means operative to cause a rapid release of the brakes on a given vehicle Wheel, means responsive to the rate of rotative deceleration of the given Wheel for effecting operation of the rapid release means at a certain rate of rotative deceleration of the Wheel or at a certain higher rate of rotative deceleration of the wheel, and means responsive to the rate of retardation of the vehicle for determining at which of said rates of rotative retardation of the wheel said responsive means will cause operation of the rapid release means.

2. A vehicle brake control equipment comprising means for effecting application and release of the brakes on the vehicle, means operative to cause rapid release of the brakes on a given vehicle wheel, means responsive to the rate of rotative deceleration of the said given wheel for effecting operation of said rapid release means at a certain rate of rotative deceleration or at a certain higher rate of rotative retardation of the given wheel, and means responsive to the rate of retardation of the vehicle effective when the rate of retardation of the vehicle is below a certain rate for causing the last said means to cause operation of the rapid release means at the said certain rate of rotative deceleration of the given wheel and when the rate of retardation of the vehicle exceeds said certain rate of vehicle retardation to cause the last said means to eiect operation of the rapid release means only at the said certain higher rate of rotative deceleration of the given wheel.

3. A vehicle brake control equipment comprising means for effecting a service application or an emergency application of the brakes on all wheels of the vehicle, means operative to cause rapid release of the brakes on a given wheel, means responsive to the rate of rotative deceleration of the said given wheel for eiecting operation of the rapid release means at a certain rate of rotative deceleration of the given wheel or at a certain higher rate of rotative deceleration of the given wheel, and means for causing the last said means to eiect operation of the rapid release means at the said certain rate of rotative deceleration of the wheel during a service application and effective to cause operation of the rapid release means at only the said certain higher rate of rotative deceleration of the Wheel during an emergency application of the brakes.

4. A vehicle brake control equipment comprising means for eiecting application and releaser of the brakes on all the wheels of the vehicle, means operative to cause rapid release of the brakes on a given wheel, means responsive to the rate of rotative deceleration of the given wheel for effecting operation of the said rapid release means whenever the rate of rotative deceleration of the given wheel exceeds a certain rate, and means effective during an emergency application of the brakes for preventing the last said means from causing operation of the rapid release means except when the given wheel decelerates rotatively at a rate in excess of a second certain rate higher than the rst said certain rate.

5. A vehicle brake control equipment comprising a brake pipe normally charged with fluid under pressure, means operative in response to a service rate of reduction of brake pipe pressure to effect a service application of the brakes on all wheels of the vehicle and in response to an emergency reduction of the pressure in the brake pipe to effect an emergency application of the brakes on all the wheels of the vehicle, means operative to cause rapid release vof the brakes on a given vehicle wheel, means operatively responsive to the rate of rotative deceleration of thegiven wheel for effecting operationfof the rapid release means at a certain rate of rotative deceleration of the given Wheel or at a certain higher rate of rotative deceleration ofthe` given wheel, and means controlled by the pressure in the brake pipe and responsive only to an emergency reduction of the pressure in the brake pipe for preventing the last said means fromvcausing operation of the said rapid release means at ythe said certain rate of rotative decelerationof the given Wheel.

6. A vehicle brake control equipment comprising means for effecting application and release of the brakes on all the Wheels of the vehicle, means operative to cause rapid release of the` brakes on the said given wheel, means responsive to the rate of rotative decelerationof the given wheel to causefoperation of the rapid release means when the rate of rotative deceleration of the given wheel exceeds a certain rate or a certain higher rate,rmeans responsive to the rate of retardation of Vthe vehicle for causing the wheel responsive means to eiect operation of the said rapid release means when the given wheel exceeds said certain rate as long as*` the rate of retardation ofthe vehicle does. not eX.-

ceed a certain rate and efective to cause the saidv wheel responsive means to effect operation of the rapid release means only when the wheel exceeds the said certain higher rate of rotative deceleration while the rate of retardation of the vehicle exceeds said certain rate, and means controlled by the Wheel responsive means for regulating the degree of application of the brakes on the said given wheel so as to cause the rotative deceleration of the given wheel at a substantially constant rate lower than` the said certain higher rate.

'7. A vehicle brake control equipment comprising means for eecting application and release of the brakes on all the wheels of the vehicle, meansl operative to cause rapid release of the brakes on the said given wheel, means responsive to the rate of rotative deceleration of the given wheel to cause operation of the rapid release means when the rate of rotative deceleration of the given wheel exceeds a certain rate or a certain higher rate, means responsive to the rate of retardation of the vehicle for causing the wheel responsive means to eect operation of the said rapid release means when the given wheel exceeds said certain rate as long as the rate of retardation of the vehicle does not exceed a certain rate and effective to cause the said wheel responsive means to effect operation of the rapid release means only when the wheel exceeds the said certain higher rate of rotative deceleration while the rate of retardation of the Vehicle exceeds said certain rate, and means controlled by the wheel responsive means for regulating the degree of application of the brakes on the said given wheel so as to cause the rotative deceleration of the given wheel at a substantially constant rate between the said certain rate and said certain higher rate of rotative deceleration.

8, In a brake control equipment for vehicles having brake devices wherein the rubbing parts possess a friction-fading characteristic, means for initiating a continually increasing` degree of application of the brakes on all Wheels of the vehicle, a plurality of means associated individually with a corresponding plurality of the vehicle wheels and operatively responsive to the rate of` rotative deceleration of the corresponding wheel, means operative under the control of any one of the said plurality of means when the associated Wheel decelerates rotatively at a rate. in excess of a certain rate for preventing further increase in the degree of application of the brakes on all the plurality of wheels, and means effective, once the last said means is operated, to prevent an increase in the degree of application notwithstanding a reduction in the rate of rotative deceleration of the car wheel below said certain rate until all of saidrplurality of wheels decelerate rotatively at a rate less than a second certain rate which is a certain amount lower than the rst said certain rate.

9. A vehicle brake control equipment comprising means for effecting applicationand release of the brakes on all the wheels of the vehicle, means operative to effect a. rapid releaseof the brakes on a given Wheel, means for effecting reapplication of the brakes on the givenWheel independently of the rst said means, a rotary inertia device associated with the said given wheel effective in response to the rotativedeceleration of the given wheel at a rate in excess of acertain rate or at a ratein excess of a certain higher rategtocauseoperation of the said-rapid release.

means and effective in response to the rotative acceleration of the Vehicle wheel at a rate in excess of a certain rate for effecting operation of said brake reapplying means, and means operatively responsive according to the rate of retardation of the vehicle for preventing said rotary inertia means from being effective to cause operation of the rapid release means except when the rate of rotative deceleration of the given wheel exceeds said certain higher rate as long as the rate of retardation of the Vehicle exceeds a certain rate.

10. In a brake control equipment for vehicles having Wheel brake devices wherein the rubbing parts possess a friction-fading characteristic, means for initiating a continually increasing degree of application of the brakes on all wheels of the vehicle, individual means for each wheel of the vehicle operatively responsiveto the rate of rotative deceleration of the corresponding Wheel, means normally conditioned to permit the increase in the degree of application of the brakes on the Wheels of the vehicle at a relatively rapid rate and operative under the control of any of the individual means when the corresponding wheel decelerates rotatively at a rate in excess of a certain rate for preventing further increase in the degree of application of the brakes except at a relatively slow rate, and means for preventing the operation of the last said means to thereafter permit an increase in the degree of application of the brakes at the said relatively rapid rate until the wheel decelerates rotatively at a rate below a second certain rate that is a predetermined uniform amount below the said certain rate.

JOSEPH C. MCCUNE. 

